Variable-speed gear



may 26,' 192s.'

H. D. WILLIAMS VARIABLE SPEED GEAR Filed July 27, 1920 3 SheetsSheet l INVENTOR. ifarvey. Mllz'ams hg2g;ATTORNEY. A

May 26, V192s. 1,53%),616

H. D. WILLIAMS VARIABLE SPEED GEAR Filed July 2'?, 1920 '3 ASheelzsSh'eea'c 2 Z7 ATTORNEY.

May 26, 1925.

H. D. WILLIAMS VARIABLE SPEED GEAR Filed July 27, 1920 3 SheetsA-Sheuet INVENTOR'.

Mlfzlams Harvey/.

j Patented May ze, 1925.

UNITED sTATEs PATENT oFFicE.'

HARVEY n. WILLIAMS, or WALLINerom'), coNNEc'rIcU'r, AssIGNon To THE WATER- BUnY 'rooL COMPANY, or WATERBURY, coNNEcTIcUT, A CORPORATION o F coN- l 2 il I n ncTIcU'r.

l VAMABLE-SPEED GEAR;

Application ala my 27, 1920.v serial No. 399,364.

To all it may concern:

Be it known that I, HARVEY D. WILLIAMS, `a citizen of the United States, and resident of Wallingford, in the county of New Ha- 8 Ven and State of Connecticut, have invented certain new and useful Improvements in Variable- Speed Gears, of which the following is a specification.

My invention relates to apparatus intended for operation with a fluid in motion, and

has been designed .chiefly for use in connection with variable speed gears of the hydraulic type, comprising a pump which zcauses liquid to be propelled and to actuate a motor, and the present invention is more particularly a development of speed gears of the general character set forth 'in Letters Patent of the United States Nos.-

893558, 925,148 and 1,044,838 granted to me on July 14, 1908, June 15, 1909, and November 19, 1912 respectively.

'The object of my invention is to improve variable speed gears of the above-indicated type, particularly in the following respects: First, with a view of decreasing the resistance within the apparatus, and enabling higher speeds to be used readily, I provide improved lubricating means which enable me to dispense with immersing some of the parts in an oil bath, as in my eariler patents. lt is highly desirable to be able to use high speeds for the pump, since certain engines such as internal combustion engines, which are frequently employed for driving the :i5 pump of the speed gear, are operated most economically at a high rate of speed, and the same characteristic of high rotary speed is present in electric motors. Therefore, especially when the pump is to be driven by an zo electric motor or by an internal combustion engine, my improvements are very valuable in that they enable the pump to be operated at the same number of revolutions as the prime motor and thus dispense with the necessity existing hitherto in such cases, of either interposing a reduction gear between the prime motor and the pump, or of einploying a prime motor of especially low speed and therefore of a heavy 'and bulky type. Second, in variable speed gears of this type as constructed hitherto, a univer` sal joint has been employed in most cases in connection with the drive shaft actuating the pump and with the driven shaft oper- 5 ated by the liquid-driven motor. Such uni- Versal joint has proved the cause of a considerable loss in eliciency, and moreover, on account of its kinematic errors, requires special and .expensive .constructions and complex dimensioning of the various parts in order to obtain compensation for such er rors.. 'Moreover, such universal joint produces a comparatively large amount of friction and consequently heat, and as the amount of power which a particular machine can transmit is limited by the temperature, it will be evident that any improvement whereby the heat developed in the machine is reduced, will correspondinglyenhance the capacit of the machine or variable speed gear. ther features of my invention will appear from the detailed description following hereinafter, and the noveltyl will beparticularly pointed out in the appended claims.

Reference is tobe had to the accompanying drawings, in which Fig. 1 is a longitudinal vertical section of a preferred embodiment of my invention, taken on line 1-1 of Fig. 2, the latter being chiefly a cross section on line 2-2 of Fig. 1, but showing a portion of the midplate in face view, saidFig. 2 being on a smaller scale ithan Fig. 1; Fig. 3 is a composite cross section of the machine, at the liquid-motor portion, the sector between the lines a and b of Fig. 3 being in section on the line 3--8 of Fig. 1, the sector between the lines b and c being in section on the line 4 of Fig. 1, the sector between the lines c and d being in section on the line 5 of Fig. 1, the sector between the lines d and e, together with -the central portion of Fig, being in section on the line ii-6 of Fig. 1, while the next three sectors are in section on the lines 7 (between lines e and f), 8 (between the lines f and g), and 9 (between the lines g and a) respectively of Fig. 1; Fig. 4 is a partial horizontal section substantially on the line IV-IV of Fig. 5; Fig. 5 is a side elevation of certain adjustable parts of 100 the pump, showing said parts'in a posit-ion different from the one in Fig. 1; and Figs. 6 and 7 are face Views of certain parts shown in Fig. 4, looking outwardly and inwardly respectively, while Fig. 8 is a partial dia- 105 gram illustrating a portion of the swashplate at. the motor end of the apparatus, looking in a direction perpendicular to the plane of rotation' of said plate, and showin the paths describedon said plate, by the yaxis of a piston rodand by the point of con.. e tact of saidpiston rod or push` rod wlth the stood swash-plate respectively.

In the embodlment of my invention shown herein, the apparatus comprises a pump and a liquid-motor driven thereby, both arplate has been mdicatedonly at the pump section, while .at the motor section va constant inclination of its swash-plate has been l assumed; again, I do not limit myself to th1s so, thenumerals with indicesy desi .parts of the pump which correspon to the parts bearing Ilike numerals, w1th` slight de ,the holes 29 are partl specific construction.

y I will firstdescribe those parte of the two sections-which are alike or substantltally a ing motor out indices. For the sake of brevity, only the motor'parts will be described in detail.

The motor shaft 2() is supportedl b ball bearings 21, 22; Mountedfon this sha t and keyed thereto in av manner that ermits a e of longitudinal free om is the cylinder arrel 23. .The key 24 extendlng dlametrically through the shaft is held therein b the taper pin 25and engages the cylinder barrel by the two diametrically op osite keyways 26 and 27, these being cutv eeper than is required by the height of the key, in order to form alpassageway 28 for the escape of lubricating oil as indicated b I'the arrow at 28. The cylinder'barrel is ored from end to end by an odd number (seven in theparticular case illustrated)-Qof-"sym metrica 1y and equally spaced holes or'cylinders 29 of uniform diameter. At oneend, closed by 4a late 30, lprovided with per orations- 31, eac of em in axial alignment withv one ofsaid holes or cylinders 29, these `perforations being the on] o nin at this end. sid ar s axial location vofv t c to the cylinder barrel 23, these two are onl loosely clamped 'together threade sleeve 32. In other respects, plate 30' is accurately articulated or fitted `to the cylinder 4barrel by means of .brass rings 33. Thesejare vshort lengths of brass to the cylinders 29 the longitudinal or arts ng the cop er rings tubing secured rigidllin annular;l vgrooves in the late 30 bycal 34. T e brass rings 33, origina loose in expanded to close fits therein;'thus, while the plate 30 has a slight freedom of move.- ment toward and from and more or less at different parts of the circumference, yet there will be maintained a4 `fluid-tightness by Virtue of the rings 3.3`

The two sec--v rod 44 to the swas plate 30', with respectthe'.

-movement bya ba ly fitted` the'V cylinders 29, are subsequently the cylinder barrel 23 :,saaele bolts 38; closing plates 39, 40` Y are locate at the ends of the motor section I and of the pump section respectively, said plates supporting the ball-bearings 21, 21 at the outer ends oftheshafts 20, 20res ectively, while themid-plate 37 supports tlie ball bearings 22, 22' at the inner ends of said shafts. The ball bearings 21, 21', 22,22y are cfa type designed to sustain a moderate amount of axial thrust, and their i disposition is such as to withstandvthrusts from oppositev directions, thus giving a definite longitudinal location to the shafts 20,

20'. The ball bearings 21, 21are however subjected continuously and intentionally to the thrust of a spring 41 or 41 respectively, which acts `through the-sleeve 32for 32 respectively, the cylinder barrel 23 or 23- respectively, and' lthe plate 30 o r 30 respectively to `press theseparts toward the midplate 37,Y while such springs'react'throu h the Washer 42 or 42 res ectively4 and t e shaftv 20 or`20 respectivel 21 or 2lv respectively. Y

Continuing the description of those parts -which are substantially the same for the y tothe bearing motor as for the pump,it will be noted that each cylinder bore 29 of the motor (this description, exce t for the reference numerals app ying e ua ly to' the pump) contains a plston 43, or receiving single force through the piston rod or pushv platel 45. In addition to its body or central tubular section '44,V this .push rod comprises two stop washers 46,

47, and end portions or heads 48, 49 screwed a fluid pressure on one side and transmitting` the `sameas. a

tothe ends ofthe said tubular section and clamping the washers in place, so that the parts-44, 46, 47, 48,' and 49 will be connected with each other rigidly. The head 49 has-'a spherical crownforjcontact with 'a hardened steel button 50, 'which is secured in the piston 43 bya calked copper ring 51, the pur- The push'rodis uided in its reciprocatory forms the inner lball race ofthis piston-in the cylinder bore.

ius-1 pose of thisco'nstruction being freedom of piston which would cause l bearingconsisting of a brass cage 52 and two rows of balls 53 and.

The cylindrical surface of the ushrod'f.

caring,

while the cylinder -wall 29 forms the youter ball race. A mits of two degrees of freedom of movement, since the pushl rod can be reciprocated .and also rotated, both motions beingfrictionless.

bearing of this character perthe sphere being at apoint 55 in the axis 4plate of the push rod. The radius of the sphere and the distance between the balls 53 and 54 are so related to each other and to the amplitude of movement or stroke of them pushrod and of the ball bearing-that the point 55 is always somewhere between the' planes of the two rows of balls. The reason fon this adjustment or relation will appearlfrom a consideration of the forces involved. The push rod is subject to two 'forces nearly opposite, that of the swash plate on one side and thatof the piston 43 on the other. The lines of action of these two forces intersect at thev point which must therefore be the point of application of the resultant which is the loadon the ball bearing. Since the resultant force is always between the two rows of balls, it follows that the yload will be divided between them and the load on one row of balls can never be greater than the resultant load. as would be the case if the point 55 fell on the same side of both rows of balls.

rlhe longitudinal movement of the push rod is twice that of the ball bearing. Hence, the movement of the push rod relatively to the ball bearing is equal to the movement ot the latter in relation to the cylinder barrel 23. This relative movement of the push rod is kept within its proper limits by the stop washers 46 and 47, which in their extreme positions come in contact \v1th the ends ot' the cage 52. Similarly, the movement or" the cage 52 1s kept withm its proper limits by the stop ring 56,

which lits into the bottom of a groove cut in the barrel 23 to a sui'ic-ient depth from the outside to intersect the cylinder bores 29. rThe spherically-curved surface of the head 4S, being merely for contact with the swash plate 45, comprises but a small part et' the 'entire sphere. it is, in fact, a Zone the colatitude of which is the tilting angle of' the swash plate. Since, as explained below, the swash plate 45 of the motor section maintains a iixed angle or inclination in the apparatus illustrated, it follows that the path of the point of contact en the head 48 will be along the arc of a small circle of the sphere. that is to sayy the point or" contact ot the head 48 with the swash 45 will always be at the. same distance 4from the longitudinal axis of the push rod, and for this reason the free end of the push rod may be made tubular or open at the motor section. as shown, which may be of advantage in that it reduces the weight and simplifies the hardening and grinding of this part.

At the pump end or sectmn of the apparatus,however, the swash plate 45 may be adjustedpto ldifferent inclinations as explained below, and take a position inclined either'to the left or to the right (Fig. 1 showing a position of extreme inclination), so that the .point of contact of the head 48 with` the swash'plate 45 may an where upon or within thesmall circlew ich is. its path-when the tilting angle isa,- maximum. The used part of the spherical surface of the head v48 will therefore .be a

polar `zone of the sphere of which said surface forms a part, and accordingly, the

free end of the v'head -48 is closed instead ofv open. v

Each of the swash plates has a flatv surface for contact with the respective push. rods, and where this flat surface intersects the axis of the shaft at the point 57 or 57 is the center of the swash plate, the axis about which this plate revolves being indicated at 57, 58 and 57 58 respectively. rlhe bearing for the rotation of the swash plate is subjected to a very considerable axial thrust 'due to the combined action of the push rods, but the radial load is quite small, being due principally to the mere weight of the parts. This thrust is taken on the conical rollers 59, 59" and transferredA tothe roller tracks 60, 60', while the having a shoulder to engage the outer edge of such sleeve, while the inner edge of the sleeve engages the swash plate, on the outer `face or back thereof. rimne inner ace of the swash plate is engaged by a holding or clamping member 66 or 66. respectively having a 'screw connection with the tubular member 61 or 61 respectively, thus holding the swash plate iny proper position to the corresponding roller track and roller bearing cage. The shafts 2G, 20 extend througzh the tubular members 61, 61 without touching them. At the pump-section of the machine, the holding member 66', whicli'clears the shaft 20 iu all positionsv bf the swash plate, has a portion of its inner surface curved spherically, the center of'said sphere being at the center 57 ot the annular at surface of the swash plate 45 which is engaged `by the ends of the push rods; ot' couise, this point 57 Ylies on the axis of the shaft 20', as stated hereinbefore. This spherically-curved inner las \ always at the same point- 57, this f k shaft 20.

45may be 1 45 may be 121/2".

3? correspondin 5 of curvature of thespjherlcal inner surface of thepholding .mem er 66 `and of the spherical outer surface of the sleeve 65v are int -may shift lengthwise on the axis o the -While the swash late 45 of the-motor section is held at a xed` angle, the inclina- -t1on of the swash late -45 at the pump section may be vari tion, inner surface of sw'ash .plate 'perpendicular to axis';of shaft) A to a maximum angle at each side of theneutral mid vposition.v I prefer to employ 'an arrangement in which, as illustrated, the maximum angle which the pumpswash plate 45' may form with a lane perpendicular tothe shaft axis, wil Vbe smaller than the angle which the motor swash plate 45 forms with such a plane; fox-instance, the motor awash plate set .at an angle of 209, while the maximum angle of the pump swashvv .plate The swash -plate 45 is secured rigidly, 'say to the closing late 39.

`For varying the inclinationof t e pump .`-swash plate 45 I have shown the following mechanismzOn its inner face the clos-..

ingy plate lis provided with `vertlcal'guide ribs 40 on opposite sides of'itscenter, and

in sliding' engagement with saidribs are movable sli e. 63 'having an internallythreaded'v boss 63 in engagement with @a threaded vcontrol shaft 64,suit'ably held at 3 6 against 'longitudinal movement, and extendingto the outside of the casing shell 36,

from zer'o (neutral posi-` su1 4 top as in. Fignll, or at the bottom, if 'the' arcuate vgrooves provided'in. lugs 60 which are projected from the roller track 60 and 63", said lugs 60 lie adjacent to the-lugs being also provided with aligning horizontal recesses to seat the outer portions of the vaxis 57', 58. mentioned hereinbefore. During the vertical adjustment of the slide 63, the point 58 has a. purely vertical movement, and since the distance from said point to the center of curvature 57 is constant, it

follows that lthe* oint'57 will have to move:

slightly lengthwise of the shaft axis dui;- ing such adjustment, and this is ft 20. It will be obvious that,the1 anle of the swash plate/ will be adjusted y the movement of theslide 63. In' itsj'extreme stoppe and supported* more firmly, b the en ement ofthe roller track`60 witha gtrigly finclined surface 63,` either at the swash plate is inclinedv in the opposite direction. l norder to` facilitate embling of the parts, the holding member 66 is formed lwith a removable cap' section 6". Y

Il' view of thefaCt that the maximum. 'angle of thepump svvashl plate `45 is alwa sv less (in the, construction shown)v than t e angle ofthe motor swash plate 45, it follows that the motor pushrods will always have a longer stroke than those of ,the pump,m

v rmitted4 mounting the sleeve to sli e on the a cpositions, the swash plate may be= r4-#outer portionsgof' the pivots aref seatedin and for this reason the pump cylinders 29', the' pump pushprods, and the ball 52v of the umpfare made shorter than-t e correspondlb to be operated by hand or otherwise. ',The slide 63has a central opening 63*`;of suiii' cient( size .-to permit thel desired vertical 'movement Without bringing such slide into contact with the shaft 20. At each side of the center the-slide 63.has two inner lugs. 63* locatedjat 'the' samelev'el, and ltwo outer. lu 63' likewise located at the sauneA level,

mg parts of the motor. f l f .Thegeneral principle ofthe 'operation of this' machine is'thesame as in'my-earlier patents, that -is to sa7y,the vmidplate 37has p two-ports 37: and 43,"fjlocated onjfg'opposite saidouterlugs being4 providedsfinl, their sid'esviifV "laf planejpassilfgg through the axis 50 'outer sui-faces, with arcuate grooves curved i. oftheshafts'20, 20 fiend thmughqthjefaxes I according to a center vor axis which. 'is hori-v 157, 58 and 57, 58', one of saidl-ports serving zontal and intersects. that of the shaft .asfa;sluction rt, vandthe other asadelivwhen the slide 63 is 'adjusted to, bring fthe ery of e pump, according to the diswash plate 45 to the neutral `or f rection in which the um swash platter-45 'tion shown in Figs. 4 and 5.v llxfnsiis 'inclined'.j-flhe-'peroration'sjllgflfcome tion, said axis of the `grooveslies in vaplane into registrysuccessively withtle 37', llperpendicularto thefshaft. Into said- 3 7" of the mi'dplate, sothatthe'liquidcan pass properly from-the pumpito thel motor, and v-iceversa,if theswasl plate'45 isinf `an inclined position duringrotationofthe i pump shaft-20',l e A It is very importa "nectijng members 80, fitted on vpivot y bolts 181'- the innerends ofwhich are'screwed or other- "wise fastened tol the inner lugs 63, while the 'tand practically *suitahlarecessesM-o'fthe outer l`u '63?,1as

1 shown bestl in Fig. 4. said angesof Si the connecting members'also `extend. into in fromiany-.change ofthe tilting angle? of ias " tial that the severalfpiston movements resultg tempt to forcibly change the aggregate volume of oil on the midplate sideV of the several pistons might result in the development of a great resistanre to the turning of the control shaft G4. This requirement of constancy of oil volume for different tilting angles is successfully met by the particular location of the ulcrum 58 on which the swash plate 45 swings relatively to the adjusting slide G3, this lfulcrum 58 being so chosen lthat the distance 57', 58 is equal to the product of the secant of the maximum tilting angle (121/20 in the particular example assumed) and the radius of the spherical part of the head 48 of the push rod.

The character of the relative motion at the point of Contact between the Push rod and the swash plate (whether at the pump or Aat the motor) is a matter of considerable iniportance. This should be, if'possible, a pure rolling motion. 'Some spinning may be permitted, but there must be no slipping Aor sliding. That a single push rod acting alone will function properly is quite evident, but

the case of several rods acting simultaneously'is not so simple. A mathematical analysis however, reveals the fact'that a plurality of push rods will function together Without the necessity of slipping or sliding and with very little spinning. In Fig. 8 I have shown a portion of the motor swash plate 45, looking perpendicularly'to its fiat contact surface, and on said surface I have indicated at 67 the curve which the point of contact with one of the push rod 'heads 48 will describe on said surface during operation of the liquid-motor. The point 67 of said curve indicates the position of the contact point when the parts Vare in the position F ig. 1. The swash plate 45 revolves faster than the cylinder barrel, the ratio of the speeds be-v ing equal to the secant of the tilting angle. ln the case shown, this corresponds approxiinately to twenty revolutions of vthe swash plate to nineteen of. the cylinder barrel. For each revolution of the cylinder barrel 23, there is a loop in the curve 67. After half a revolution of the cylinder barrel in the direction of the arrow, the int of contact will have moved to the point 67 on the path, and will then 4be at the lower portion of the machine, as indicated at 68 in Fig. 1; that is to say, the point 68 in Fig. 1 indicates the location ofthe point of 'contact between the head 48 and the swash plate 45 at the time the head 48, in tracing the curve 67 on.the surface of the swash plate, rear-he the point 67 of the said'curve. All the outermost points of this curve, correspond-- ing in position to the point G7, represent positions traced when the point of contact is at Athe lo'werniost portion of the swash plate that is to say at the point 68,' vertically below the axis of the shaft 20, while all Pump a the innermost points of the curve 67 (such as 67 in Fig. 8) represent positions traced when the point of contact is in the uppermost position which it ever takes,'that isto say, vertically above the axis of the shaft 20, as indicated at 67 in Fig. 1. The curve 67 is a parallel t0 an epicycloid 69 which is the path of the oint where the axis-70 of the push rod pro onged intersects the surface of the swash plate. When the push rod is at the middle of its stroke, it'has a pure rolling contact with the swash plate, the axis 7 O'atsuch times being .at one of the cusps 69* 'of the epicycloid-69. The points. 67 and 69 are traced simultaneously, and the same remark will apply t0 the points 67 and 69". At all times when the push rod is not at the middle of its stroke, it has .a spinning motion which varies harmonically, attaining its maximum value when the push rod is at the end of its stroke (positions 67', 67 The spinning motion is accompanied Aproportionally by a rotation of the lpush ro in the cylinder barrel the amplitude of which, about one-sixteenth of a revolution in the case shown, is significant of the small amount of the spinning` motion at the contact point; .t

As a connector between the piston and the swash plate, the push rod can function as a strut but not as a tie. Its inability'to act as a tie necessitates some other provision for ymaintainin the parts vin contact. Especialinertia of the pistons, push rods, and ball: bearings. This pressure vis generated by the chamber gear'replenishingpump 71 and is transmitted to the working uid through the pipe 7 2 and the replenishing valves 73 to the ports 37', 37 in the midplate. The fact that the pressure port only which for the time being is the low-pressure port (that is to say, the port throu h which the liquid returns to the necessitates a check valve, such as 73, in the connections of both ports, see Fig. 2.- The volumetric capacity of the replenishing pump is somewhat in excess .of the normal leakage of theJ` Working` fluid, the excess passing oli' by way of the pipe 74 and d the safety valve 75, the adjustable spring of `which provides a means for realizing the suiciency of the pressure.

With a positive pressure at all times iii the working fluid, itis no longer necessary `to immerse all the working parts in oil in order to prevent the pistons from sucking air (it being understood that oil is generally ies can be transmitted to that 'I employed las the workin fluid). l Accordl .the machine. At the pump end, the saf'et valve 75 by its construction and location is made to function as an oil spra lubricator for all working parts at this en ofthe machine. The drainage from both ends or sections of the machine flows by gravity into the reservoir 78 underneath the pump section, from'which reservoir the replenishing pump 71 gets its supply.

In certain cases where the s ed gearremains idle for long periodsv uring which the working fluid' might drain away from` the cylinders and be replaced by air, it may be desirable 'to provide a storage reservoir (indicated diagrammatically at 79 as connected with the pipe 74), which may be in,

the nature of an accumulator or of-an air chamber or of an open tank at an elevation. It will be understood that each of the two sections of the machine is fully operative by itself, and also that each of thesesections is reversible in function, and mi ht beused either as a pump to propel a'liiiid, or as a motor driven by a fluid under pressure. Thus, I might remove all the arts shown atthe right of the mid-plate 3 or all the parts shown at the left of such mid-plate, and use the remaining section or apparatus as a pump, one of the mid-plate ports forming a suction port, and the other a delivery i might be, used as a motor,

inders extending lengthwise of its port; 0r' the same section on apparatus b admitting a fluid uderpressurethrough one 'of the mid-plate ports, and using the other midplate port asA an exhaust port.

I claim as my invention:

an apparatus for operation with a uid in motion, alrotary barrel having cylaxis 'of rotation, pistons arranged to reciprocate in l said cylinders, push rods in operative rela- 4said cylinders,

tion to said pistons within the .cylinders but put of-contact with the cylinder walls,-balls interposed between said push rods vand the tive cylinder walls, and a rotary plate.

res inc 'ned to the barrel axis and operatively related to said push rods.

.A V2.` In anapparatus-for operation with a fluid in motion2 a rotary barrel Ihavi uid `in motion, a rotax' barrel having cylinders extending lengt wise of' its axis of rotation, pistons arranged to reciprocate in push rods inoperative relato said pistonswithin the cylinders lbut v of rotation, recip -within said cyhnders and Vhaving end sur- Afaces `forming part of spheres the centers of out of contact with the cylinder walls, at

bearing memberl interposed between v'each push rod and the respective cylinder wall,l

and movable lengthwise in relation both to the barrel and to the push rod, and a rotary plate inclined to the' barrel axis and opery within said cylinders and having ends with surfaces forming art of spheres the centers Of which are on t e longitudinal axes of .the respective members and remain within said cylinders in every operative position of the reci i'ocatory members, and an inclined plate hel to rotate with s'aid barrel and engagingV said pherically-curved end surfaces.

5. n an apparatus for operation with a Huid in motion, a rotary barrel lhaving cylinders extending lengthwise of its axis of rotation, reci rocatory members arranged within said cy inders, a bearing member in terposed between each oi said members and the corresponding c linder and movable lengthwise relatively oth to the barrel and to the reciprocatory member, and a rotary inclined plate operatively related to said reciprocatory members.

6. In an apparatus for operation with a fluid in motion -a rotary barrel having cylinders extending lengthwise lof its axis of rotation, reciprocatory members arranged `within said cylinders and having end sur-v faces' forming part of spheres the centers'of which are on the longitudinal yaxes of the respective members, a bearing interposed between each of said reciprocatory members an apparatus or operation with a eisy and movable lengthwise in relation both to cylinders .extending lengthwise of its axis rocatory members arranged land the wall of the correspondingcylinder, d l

which are on the longitudinal axes ofthe respective members, 'a cage interposed between each of said reciprocatory members and-the wall of the corresponding cylinder, said'cage having rows of balls at its ends, in engagement with the reciprooatory member and with the cylinder wall, and being movable lengthwise relatively both to the barrel and to said member, and a rotary plate inclined to the barrel axis and engaging the spherically-curved end surfaces of sald members, said sphere centers always remaining between the planes of the two rows of bearing balls.

8. In an apparatus for operation with a fluid in motion, a rotary barrel having cylinders extending lengthwise of its axis of rotation, reciprocatory members arranged within said cylinders, a cage interposed between each of said reciprocatory members and the wallof the correspondingcylinder, said cage having rolling elements engaging simultaneously the cylinder wall and the reciprocatory member, and being movable lengthwise relatively both to the barrel and to the said member, and a rotary plate inclined to the barrel axis and operatively related to said reciprocatory members.

9. In an apparatus for operation with a fluid. in motion, a rotar barrel having cylinders extending lengt iwise of its axisl of rotation, reciprocatory members arranged in said cylinders, a bearin member interposed between each of said members and the corresponding cylinder' and .movable lengthwiserelatively both to the barrel and to the reciprocatory member, means for limiting the movement of such bearing member relatively to the cylinder barre and a rotary plate inclined to the barrel axis and operatively related to said reciproeatcry members,

`10. In an apparatus for operation with-a fluid in motion, a rotary barrel having cylinders extending lengthwise of its axis of rotation, reciprocatory members arranged in said cylinders, a bearing member interposed between each of said'members and the corresponding cylinder wall and movable lengthwise relatively both to the barrel and to the reciprocatory member, means for.

limiting the movement of such bearing member relativel to the corresponding reciprocatory mem r, anda rotary plate inclined to the barrel axis and operatively related to said reciprocatory members.

11. In an apparatus for operation with a fluid in motion, a rotary barrel Ihaving cylinders extending lengthwise of its axis of rotation,reciprocatory members arranged in said cylinders, a. bearing interposed between each of said members and the wall of the corresponding cylinder, and movable lengthwise relatively both to the barrel and to such member, separate means for limiting faces rounded accordin` the movement of each bearing relatively to I,the corresponding reciprocatory member and to thebarrel respectively, fand a rotary diameter than the cylinders, in permanent registry with said cylinders and insuccessive registry with the ports of sald stationary member, reciprocatory members in said cylinders, and rotary means operatively related to said members and inclined to thebarrel axis.

13. In an apparatus for operation with a i fluid in motion, a rotary t barrel 4having cylinders extending lengthwlse of its axis ot' rotation, a stationary ported member adapted for cooperation with said barrel but' spaced ,v therefrom, a plateA connected vwith said barrel and interposed between said station-aryl member and the barrel, said plate having perforations in registry with the cylinders of the barrel and\ adapted for registry with the ports of said stationary member, a shaft held to turn with said barrel, and a spring arrange L to press -the barrel and plate toward said stationary member, and the shaft in the opposite direc-l tion.

14. In an apparatus for operation with a iuid in mot-ion, a rotary barrel having cylinders extending lengthwise of its axis of rotation, a stationary ported member ada-pted to cooperate with the said barrel but spaced' therefrom, a plate connected with said barrel and interposed between said stationary member and the barrel, and'having perforations in registry with said cylinders and adaptedv for registry with the ports oi said stationary member, and a spring Aar-. ranged to press the barrel and plate toward said stationary member.

15. In an apparatus for operation with a fluid in motion, a rotary barrel having cylinders extending lengthwise of the axis of rotation, reciprocatory members arranged in said cylinders and havingheads with surto spheres the centers of which are on theV longitudinal axes of said members, and a plate arranged to rotate in Contact with saidv sphericallyrounded surfaces, about an axis which is inof the barrel, by 'swinging said' plate on a fulcrum transverse to sald axes, the distance of said fulcrum from the point of Inl fclinable to form different angles with that p intersection of the 'contact plane oi said late with said reciprocatory members, being equal to the product of the secant of the maximum angle to which said plate may -be inclined and the radius of the spheres according to which the contact ends of the t reclprocatory members are curved.

which said plate is fulcrumed about an axis transverse to the first-named axes, the distance of said fulcrum axis from the point of intersection of the contact surface of said plate with said-reciprocatory members, being equal to the product of the secant of the maximum angle to which said plate may be inclined and the radius'of said spherv ically-curved contact ends of the reciprocatory members.

17 `In an apparatus for operation with a iuid in motion, a rotary barrel having cylinders extending lengthwise of its axis of rotation, reci rocatory members in-said cylinders, a lsha t co-axial with the barrel and rotating therewithf'a sleeve mounted toslide lengthwise onsaid shaft and having its outer surface curved accordin to a portion of a sphere the centerfof w ich is on the axis of the shaft, a rotary plate in operative relation to said reciprocatory members and having a sphericall curved 'socket mounted on said sleeve, an a slide movable transversely to the barrel axis, said rotary" plate being fulcrumedon s'a'idvslide toi swing about an axis transverse-both to the path of the slide and to the axis of the barrel.

18. In apparatus for operation with a fluid in motion, a rotary barrel having cylinders extendingl lengthwise of its axis of rotation, reciprocatory members in said cylinders, a member supported to move lengthwise of the barrel axis and having'its outer surface curved according to a portion of a sphere the center ofwhlch is onv the barrel axis, a rotary plate in o rative relation to said reciprocator ,mem ers and having a v spherical y-curve socket mounted on said member, and a control member movable transversely to the barrel axis, said rotary late being fulcrumed on said control memr to swing about an axis transverse both to the path of said control member and to the axis of the barrel. Y

AIn testimony whereof, I have signed this specification.

i HARVEY D. WILLIAMS. 

